Laser with Brayton cycle outlet pump

ABSTRACT

A chemical oxygen-iodine laser (COIL) comprises an oxygen generator and a nozzle for accelerating generated oxygen to a high or supersonic velocity. A laser cavity is coupled to the nozzle, wherein the accelerated fluid, with injected iodine, is employed as a laser gain medium. A Brayton cycle outlet pump employs the accelerated oxygen and iodine as a component of a process fluid in a Brayton cycle to raise the static pressure of the accelerated fluid to ambient conditions. The Brayton cycle pump comprises a compressor having an inlet and an outlet, the inlet being coupled to the laser cavity to receive and compress accelerated oxygen. A combustor is coupled to the outlet of the compressor to receive compressed oxygen and ignite and combust it A turbine is coupled to the outlet of the combustor to expand the ignited and combusted gas, wherein the turbine powers the compressor. Multiple reheat stages may be used and regeneration and intercooling may also be used. The use of reheat, regeneration, and intercooling depends on the application.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a continuation of U.S. patent application Ser. No. 10/874,039, entitled “LASER WITH BRAYTON CYCLE OUTLET PUMP” filed on Jun. 22, 2004, which is hereby incorporated by reference for all purposes.

TECHNICAL FIELD

This application relates to a method and apparatus for increasing the pressure of a gas exiting a chemical oxygen-iodine laser.

BACKGROUND

The chemical oxygen-iodine laser (COIL) is undergoing development as the high-performance laser of choice for target interdiction. In this laser, a supersonic flow of singlet delta oxygen is used with iodine as the gain medium in the laser cavity of a continuous wave (cw) chemical laser. A chemical gas laser according to the invention involves a steady, supersonic, low-pressure gaseous flow inside the laser cavity. In fact, all high-performance cw chemical lasers operate supersonically with a laser cavity pressure of a few Torr. For example, a COIL typically operates in the 1 to 10 Torr range, although pressures as high as 20 Torr may be possible. A pressure value above about 4 Torr is usually achieved by adding diluent gas to the singlet oxygen generator (SOG) that drives the COIL device. A diffuser is then used to increase the device's exit pressure. If this pressure is still below ambient, the diffuser is followed by a pumping system that typically consists of mechanical pumps or an ejector system. (In specialized cases, chemical pumping may be used.) The type of high-performance laser under consideration may potentially be mounted on a motorized vehicle, naval vessel, or on an aircraft. It requires a pressure recovery system to move the high-speed, spent laser gas from its several Torr value to a pressure level slightly above ambient. At sea level, ambient is 760 Torr, while ambient for an aircraft at a 40,000 foot altitude would be close to 150 Torr. Thus, due to the pressure differential, pressure recovery presents a challenge. In any case, the size and weight of the pressure recovery system is significant to the viability of the overall laser system. It is thus important that the pressure recovery system be as compact and lightweight as possible for the intended application.

In a laboratory, mechanical pumps are used for pressure enhancement, but these are certainly not compact or lightweight. Outside of the laboratory, ejectors are typically utilized. The ejector system, however, may require multiple stages and is both bulky and heavy. In special cases, where the laser run time and power are limited, a bulky chemical pump system can be used.

Accordingly, there is a need for a relatively compact or lightweight pressure recovery system for increasing the pressure of a gas used in a chemical oxygen-iodine laser so that the gas may be brought to ambient pressure.

SUMMARY

It is a general object of the present invention to provide a chemical gas laser with a means for raising the high-velocity, low-pressure lasing or gain medium to ambient conditions. This and other objects of the present invention are achieved by providing a chemical oxygen-iodine laser (COIL) that comprises an oxygen generator and a nozzle for accelerating generated oxygen to a high or supersonic velocity. A laser cavity is coupled to the nozzle, wherein the accelerated oxygen, with injected iodine, is employed as a laser gain medium. A Brayton cycle outlet pump employs the accelerated oxygen and iodine as a component of a process fluid in a Brayton cycle to raise the static pressure of the accelerated oxygen and iodine to ambient conditions.

According to the preferred embodiment of the present invention, the Brayton cycle pump comprises a compressor having an inlet and an outlet, the inlet being coupled to the laser cavity to receive and compress accelerated oxygen. A combustor is coupled to the outlet of the compressor to receive compressed oxygen and ignite and combust it. A turbine is coupled to the outlet of the combustor to expand the ignited and combusted gas, wherein the turbine powers the compressor.

According to the preferred embodiment of the present invention, a diffuser between the laser cavity and the Brayton cycle outlet pump is used to decelerate the flow of oxygen and iodine from supersonic velocity.

According to the preferred embodiment of the present invention the Brayton cycle outlet pump comprises multiple stages of compressors, combustors, and turbines.

According to the preferred embodiment of the present invention the Brayton cycle outlet pump includes a reheat stage.

According to the preferred embodiment of the present invention, the Brayton cycle outlet pump includes a regeneration stage.

According to the preferred embodiment of the present invention, the turbine has a work output that exceeds the work required to operate the compressor, wherein there is net work output from the Brayton cycle pump.

Other objects, features, and advantages of the present invention will become apparent with reference to the drawings and the detailed description, which follow.

BRIEF DESCRIPTION OF THE DRAWINGS

For a more complete understanding of the present invention, and the advantages thereof, reference is now made to the following descriptions taken in conjunction with the accompanying drawings, in which:

FIG. 1 a is a schematic diagram of a chemical laser system including a diffuser and a Brayton cycle pump.

FIG. 1 b is a schematic diagram of an alternative embodiment of a chemical laser system including a diffuser and a Brayton cycle pump.

FIG. 2 is a schematic diagram of a Brayton cycle pump that may be used with a chemical oxygen iodine laser.

FIG. 3 a is a temperature-entropy diagram for the Brayton cycle of FIG. 2.

FIG. 3 b is a temperature-entropy diagram for the Brayton cycle of FIG. 2 with regeneration.

DETAILED DESCRIPTION

Shown in FIG. 1 is a chemical oxygen iodine laser (COIL) system. A singlet oxygen generator (“SOG”) 12 generates singlet delta oxygen for the laser. The SOG is preferably constructed according to U.S. patent application Ser. No. 10/453,148, although other SOG's are known and may be used. The singlet delta oxygen, which may contain a diluent and other constituents (collectively “gas”), flows from the SOG through the laser nozzle 14. The gas typically comprises oxygen, water vapor, iodine, helium, chlorine and possibly SOG diluent. The gas flows through an optical or laser cavity 16 at supersonic velocity and at a pressure typically between 1 and 10 Torr, although pressures as high as 20 Torr may be possible.

After passing through the laser or optical cavity 16, the gas continues, preferably, to a diffuser 18 followed by a Brayton cycle (which is a gas cycle) outlet pump (“BCP”) 22 according to the present invention. A BCP is a Brayton cycle engine or heat engine configured to use the gas exiting the optical cavity and diffuser 18 as the oxygen source for the engine. If flow through the laser or optical cavity is supersonic, a diffuser must be used to decelerate the fluid prior to entry into the BCP to avoid a shock system in or upstream of the optical cavity. The BCP is configured as a pump so that the BCP exhaust will be at a higher pressure than the pressure of the gas entering the BCP. The diffuser 18 and BCP 22 each act to raise the pressure of the gas so that, upon exiting the BCP 22, the stagnation pressure of the gas will be greater than the ambient pressure and the gas may be vented to the atmosphere, a storage unit (not shown) or additional processing equipment (not shown). The diffuser 18 is preferably designed as described in a copending application entitled “Supersonic Diffuser,” Ser. No. 10/874,040, filed concurrently herewith.

FIG. 2 is a schematic of a BCP that is used to further enhance the pressure of gas exiting the diffuser 18. The gas enters a compressor 52, which compresses or raises the pressure of the gas. The compressor 52 may be an axial, radial or reciprocating compressor or any other compressor suitable for raising the pressure of the effluent. The compressor 52 may include only a single compression stage or several compression stages. Preferably, the compressor 52 is a single-stage compressor with axial inflow and radial outflow. The gas entering the compressor 52 may be at the operating pressure of the laser if the laser flow is subsonic. In the case of supersonic flow in the laser cavity, the pressure of the gas is increased by the diffuser, the magnitude of the increase depending on the Mach number of the fluid entering the diffuser and the efficiency of the diffuser.

After the gas is compressed, it is passed to a first combustor 54. In the first combustor 54, fuel from a fuel source 55 is mixed with the gas and ignited. The fuel is preferably a hydrocarbon fuel, although other fuels are known and may be used. If the COIL is installed in an aircraft or other vehicle, the vehicle fuel may also be used to fuel the BCP. The fuel source 55 may be a dedicated fuel tank, a vehicle fuel tank for COIL installed in an aircraft or other vehicle, or another fuel source.

Upon exiting the combustor 54, the hot gas passes to a first turbine 56, which converts the elevated enthalpy of the gas into mechanical work through expansion. The first turbine 56 may be an axial or radial turbine or any other turbine suitable for efficiently converting the elevated enthalpy of the effluent into mechanical work. The first turbine 56 may include only a single expansion stage or several expansion stages. Preferably, the first turbine 56 is a single stage turbine with radial inflow and axial outflow.

In order to provide additional power, a reheat stage may be used, if needed, after the first turbine 56. If reheat is used, the gas passes from the first turbine 56 to a second combustor 58. In the second combustor 58, fuel is again added to the gas and ignited, raising the enthalpy of the gas. The fuel is preferably the same fuel used in the first combustor 54, although other fuels may be used.

The gas passes from the second combustor 58 (reheat stage) to a second turbine 62. The second turbine 62 may be an axial or radial turbine or any other turbine suitable for efficiently converting the elevated enthalpy of the effluent into mechanical work. The second turbine 62 may include only a single expansion stage or several expansion stages. In some cases, particularly where the COIL is being used at an elevated altitude or with a diffuser of the type described in co-pending application “Supersonic Diffuser,” Ser. No. 10/874,040, filed Jun. 22, 2004, the reheat stage (second combustor 58 and the second turbine 62) may not be necessary.

FIG. 3 a is a temperature-entropy (T-s) diagram corresponding to the BCP of FIG. 2. FIG. 3 b is the same as FIG. 3 a, except for the provision of a regenerator. As indicated, the FIG. 2 BCP has two combustors, two turbines, and no regeneration.

A control system (not shown) regulates the fuel flow rate in coordination with the operation of the laser so that the pressure of the effluent at the exit of the second turbine 62 (or the first turbine 56 if a second turbine is not used) is slightly higher than the ambient pressure, allowing the gas to be vented. In addition, the fuel flow rate is regulated so that the maximum turbine inlet temperature does not exceed T_(m).

The following is a detailed example of an embodiment of certain aspects of the present invention. As indicated, the FIG. 2 BCP has two combustors, two turbines, and no regeneration. The reference numerals 102-112 refer to the gas conditions at each point in the BCP, e.g., T₁₀₂ is the gas temperature at the entrance to the compressor 52 and p₁₁₂ is the gas pressure at the exit of the second turbine 62.

A Brayton cycle can be operated with reheat, regeneration, and intercooling. With reheat, more than one combustor/turbine pair is used. Let n represent the number of combustor/turbine pairs, i.e., the number, minus one, of reheat stages. In the BCP model developed for the subsequent analysis, n can range from unity to five. FIG. 2 shows a single reheat stage; hence, n=2. The primary function of reheat is to increase the magnitude of turbine output power. Without reheat, the turbine power may be insufficient for driving the compressor 52.

Regeneration utilizes the hot gas from the exit of the last turbine stage, state 112 in FIG. 2, to heat the gas exiting the compressor 52 at state 104. A regenerator is usually a counterflow heat exchanger. The principal function of a regenerator is to reduce the fuel flow rate. This is evident by comparing FIG. 3 a with FIG. 3 b. The first combustor 54, see FIG. 3 a, requires enough fuel to increase the temperature from T₁₀₄ to T₁₀₆, where T₁₀₆ equals the maximum cycle temperature, T_(m). In FIG. 3 b, less fuel is now required to increase the temperature from T_(x) to T₁₀₆. Regeneration thus reduces the fuel flow rate to the first combustor 54, which otherwise requires much more fuel than the second (reheat) combustor 58. Regeneration is particularly effective in reducing the fuel flow rate when n is one or two and T₁₀₄ is well below T₁₀₆. As the compressor pressure ratio increases T₁₀₆-T₁₀₄ decreases and regeneration becomes less effective.

When a BCP is used as an auxiliary power unit (“APU,” wherein the work output of the turbines exceed the work required to operate the compressor, thereby generating net work or power output), regeneration typically has a major impact on the cycle efficiency by reducing the heat input. (The power output also decreases slightly.) Cycle conditions in the subsequent analysis may appear to favor the use of regeneration. On the surface, the system trade-off associated with regeneration is the size and weight of the heat exchanger and ducting versus the reduction in fuel. A more relevant system comparison, as will be shown, is between the fuel flow rate, with or without regeneration, versus the basic hydrogen peroxide COIL flow rate.

In power engineering, the term “stage” sometimes has two distinct meanings. For instance, a single axial flow turbine may be said to have 10 stator/rotor stages. As used herein, the term stage refers to a single component, regardless of the number of stators or rotors. For example, if n=3, the BCP has three turbine stages. Similarly, if the compression ratio across the compressor is 49, the compression may be provided by two (centrifugal) in-line compressors, each with a compression ratio of 7, for example.

The approach here differs from standard Brayton cycle practice in that the BCP is primarily used as a pump, the inlet and exit pressures generally differ, and a complete combustion assumption is used for the oxygen/methane combustion rather than the simpler, less accurate, and inappropriate air-standard or cold air-standard approaches. The complete combustion assumption is needed if fuel and oxygen consumption rates are to be evaluated.

Metallurgical constraints set a limit on the turbine inlet temperature. This temperature is denoted as T_(m) and is the maximum cycle temperature and the inlet temperature to each turbine stage in the BCP. The value of T_(m) depends on the material the turbine is constructed with, its surface coating, whether blade cooling is used, the design of such cooling, and the like.

The BCP is preferably constructed according to the principles of the NASA-funded design study entitled, “Advanced General Aviation Turbine Engine (GATE) Study” The GATE study resulted in a recommendation that blade cooling not be used and that 1504 K represents a maximum turbine inlet temperature for uncooled blades. Therefore, uncooled blades are used in the BCP analysis according to the present invention with a maximum turbine inlet temperature of 1500 K. A typical GATE turbine stage has a radial inflow and an axial outflow with a maximum pressure ratio of 12. In the pump application, where the turbine pressure ratio is significantly smaller than the compressor ratio, and with reheat, the maximum turbine pressure ratio of 12 easily satisfies the cases discussed here.

For compressors, GATE examined a variety of configurations, centered about the use of a radial outflow centrifugal component. A single radial outflow component can have a pressure ratio as large as 9, as compared to a purely axial unit where the maximum pressure ratio is significantly less. GATE examined the performance of a radial, axial-radial, triple axial-radial, and twin radial compressors. They suggest that by 1985, an axial-radial unit can have a maximum pressure ratio of about 14.8 with an efficiency of 85%. For a somewhat higher pressure ratio, several axial units, upstream of the centrifugal unit, would be used. Starting at a pressure ratio above about 20, two, in-line, centrifugal units would be required. Because of the high inlet temperature to the second compressor, intercooling is recommended, in order to significantly decrease the inlet volumetric flow rate. This decreases the diameter of the compressor and improves its performance.

Detailed analysis shows that using the gaseous inlet flow, which is near 300 K at state 102, for intercooling is counter-productive. There is, however, a substantial, ready source of near-room-temperature liquid coolant. This is the dilute, spent BHP from the SOG. For reasons of simplicity, the cycle analysis does not consider intercooling.

Regardless of the number, or type, of compressor stages, the overall compression ratio is $\begin{matrix} {{P_{c} = \frac{p_{104}}{p_{102}}}{or}} & \left( {1a} \right) \\ {P_{c} = \frac{p_{x}}{p_{102}}} & \left( {1b} \right) \end{matrix}$ when a regenerator is present. The P_(c) values associated with aircraft and satellite-based operation are quite modest and a single compressor stage suffices. The P_(c) value for sea-level operation is larger, and the compressor 52 may require one, or more, axial units, or a second centrifugal unit.

The assumptions for the following example cases are briefly summarized: A steady flow of a mixture of ideal gases is used with a modified Brayton cycle. The cycle may have regeneration and reheat, but no intercooling or internal turbine blade cooling. Each of the physical units, such as a combustor 54, 58 or a turbine 56, 62, is assumed to be adiabatic. The compressor 52, turbines 56, 62, and regenerator, however, have assigned efficiencies. When more than one turbine stage is present, the pressure ratio across each stage is the same. This maximizes the turbine output power.

For analytical convenience, methane is the fuel; it is viewed as a surrogate for hydrogen or any typical hydrocarbon fuel. Although COIL may, or may not, have an inert diluent, no diluent is explicitly considered, i.e., at the BCP inlet the gas is pure oxygen. This is not a significant factor, since, typically, less than 15% of the oxygen is burned; the remainder, in effect, is diluent. Complete combustion is assumed. In the model, this means that only O₂, H₂O, and CO₂ exit a combustor. A turbine inlet temperature of 1500 K is specified for each turbine stage.

In practice, other fluids (liquid or gas) enter compressor 102. Relative to the oxygen, they have small molar flow rates. These fluids include water vapor, iodine, helium, and possibly a trace amount of chlorine. These constituents have, at most, a minor effect on the performance of a BCP. With a COIL plus diffuser based on my copending application Ser. Nos. 10/453,148, 10/658,569 and the Supersonic Diffuser disclosure, the need for SOG diluent is unlikely, even for sea-level operation. As noted earlier, a BCP can still be used even when there is a significant SOG molar flow rate of diluent, for any desired diluent.

The subscript j, j=1, 2, 3, 4, denotes the species, as given below in table 1, where W_(j) is the molecular weight of species j. TABLE 1 j species W_(j) (kg/kmol) 1 O₂ 31.9988 2 CH₄ 16.04246 3 H₂O 18.01528 4 CO₂ 44.0095

The i subscript denotes the states. States are numbered 102-112, as shown in FIGS. 2, 3 a and 3 b.

Prescribed model parameters are

-   -   p₁₀₂, T₁₀₂, T_(m), p_(a), P_(c), n, η_(c), η_(t), η_(rg)

The pressure and temperature of the compressor inlet, state 102, are given. The calculation throughout is normalized by an assumed, convenient oxygen molar flow rate of 1 kmol/s at the inlet to the compressor. Consequently, the inlet mass flow rate, in units of kg/s, is {dot over (m)}₁₀₂=W₁   (2) which is a huge flow rate for a COIL. An actual large COIL might have a flow rate of 0.1W₁, in which case all computed flow rates, heat transfer rates, and powers are multiplied by 0.1.

The maximum cycle temperature, T_(m), is both the combustor 54, 58 exit temperature and the turbine 56, 62 inlet temperature. The ambient pressure is p_(a), while P_(c) is the prescribed compressor 52 pressure ratio, p₁₀₄/p₁₀₂. As previously noted, n is the number of combustor/turbine pairs, or stages. The parameters η_(c), η_(t), and η_(rg) are the compressor 52, turbine 56, 62, and regenerator efficiencies, respectively. As a matter of convenience, η_(c) equals η_(t), where η_(t) applies to each turbine stage.

The k subscript denotes a particular combustor/turbine pair, and k ranges from unity to n. The one exception is the first combustor when regeneration is present. In this case, the first combustor inlet temperature is T_(x). The first combustor 54 exit state, which is also a turbine inlet state, is denoted as 106, while the first turbine exit state is 108.

As is standard thermodynamic practice for compressors and turbines, an isentropic calculation is first performed in order to obtain an isentropic exit enthalpy, denoted as h_(is). Thus, h_(104s) and h_(108s) are the isentropic enthalpies at the exit of the compressor and first turbine stage, respectively. The actual enthalpies stem from the component efficiency definitions, written as $\begin{matrix} {h_{104} = {h_{102} + {\frac{1}{\eta_{c}}\left( {h_{104s} - h_{102}} \right)}}} & (3) \\ {{{h_{104 + {4k}} = {h_{102 + {4k}} - {\eta_{t}\left( {h_{102 + {4k}} - h_{{104 + {4k}},s}} \right)}}},{k = 1},2,\ldots\quad,n}{where}} & (4) \\ {{T_{102 + {4k}} = T_{m}},{k = 1},2,\ldots\quad,n} & (5) \end{matrix}$ It is computationally convenient to use temperatures, instead of enthalpies, for the prescribed regenerator efficiency $\begin{matrix} {\eta_{rg} = \frac{T_{x} - T_{104}}{T_{104 + {4n}} - T_{104}}} & \left( {6a} \right) \end{matrix}$ which is used as T _(x) =T ₁₀₄+η_(rg)(T _(104+4n) −T ₁₀₄)   (6b) Note that if η_(rg)=0, then T_(x)=T₁₀₄ and regeneration is, in effect, not used. If η_(rg)=1, then T_(x)=T_(104+4n) and T_(x) has its optimum value. The second law requires T₁₀₄≦T_(y), T_(x)≦T_(104+4n)   (7) Nevertheless, the computer model can violate these strictures when P_(c) becomes quite large, say 60. In this circumstance, the compressor outlet temperature, T₁₀₄, can exceed the turbine outlet temperature, T_(104+4n). Of course, regeneration is then not permissible. This result is consistent with the earlier statement that regeneration loses effectiveness when P_(c) becomes large.

In the model, cycle performance is first computed without regeneration. The regeneration calculation then uses several estimates from the earlier computation; they are denoted with an overbar. In particular, T_(x) is obtained this way, i.e., T _(x) =T ₁₀₄+η_(rg)( T _(104+4n) −T ₁₀₄)   (8) The actual regenerator efficiency, η′_(rg), that corresponds to this T_(x) value is given by Eq. (6a), where T_(104+4n) is the actual last turbine exit temperature for a cycle with regeneration. The two regeneration efficiencies differ only slightly, since T_(104+4n) hardly changes with regeneration.

Because the gas mixture is ideal, but is not a perfect gas mixture with constant specific heat values, a number of temperature values require an iterative numerical solution. These values are readily obtained using any standard root-solving routine. The routine utilized in the model requires a first estimate for the unknown; this is easily provided.

Only oxygen and methane at T₁₀₂ enter the first combustor 54. Sufficient methane is added to raise the exit temperature of the first combustor 54 to T_(m). For the first combustor 54, a distinction is made between the non-regenerative and regenerative cases. Subsequent combustors do not require this distinction. For the second combustor 58, the entering gas consists of oxygen, water vapor, and CO₂ from the preceding combustion, and methane gas, which again enters from the fuel source 55 with an assumed T₁₀₂ temperature. As before, sufficient methane is added to raise the exit temperature to T_(m). An energy balance equation, for each combustor, is used to determine a compositional variable, χ_(n), that is comparable to an equivalence ratio. Aside from this parameter, the heat produced and mass flow rate of methane, per combustor, are evaluated. The heat-produced parameter is only used in the evaluation of a cycle efficiency. A k-loop is also described. The function of the loop is to establish values for parameters, such as T_(104+4k), for each combustor/turbine pair.

Each turbine has an inlet temperature T_(m) and an outlet state determined by a pressure ratio, P_(t), given later, that is equivalent to specifying its outlet pressure. The computation is performed inside the k-loop with the final item being the turbine power, {dot over (W)}_(tk), for the k^(th) stage.

The regenerator temperature, T_(x), is given by Eq. (8). After the k-loop is performed, the actual regenerator efficiency $\begin{matrix} {\eta_{rg}^{\prime} = \frac{T_{x} - T_{104}}{T_{104 + {4n}} - T_{104}}} & (9) \end{matrix}$ is evaluated. As previously noted, T_(104+4n) is close to T _(104+4n) for all n values, even when n=1. Hence, η_(rg) and η′_(rg) are also close. A regenerator energy balance provides T_(y). It has the form F ₅(T _(y))=(1−2χ_(n))H ₁(T _(y))+2χ_(n) H ₃(T _(y))+χ_(n) H ₄(T _(y))−f ₅=0   (10a) where f ₅=(1−2χ_(n))H ₁(T _(104+4n))+2χ_(n) H ₃(T _(104+4n))+χ_(n) H ₄(T _(104+4n))−H ₁(T _(x))+H ₁(T ₁₀₄)   (10b) A first estimate for T_(y) is given by T _(y) ⁽¹⁾ =T ₁₀₄ +T _(104+4n) −T _(x)   (10c)

In the above, H_(i) (T) is the ideal gas enthalpy of species i at temperature T. This enthalpy includes the heat of formation. The compositional variable χ_(k) is given by: χ₀=0, χ_(k)=(1−2χ_(k−1))φ_(k)+χ_(k−1) , k=1, 2, . . . , n where the equivalence ratio is ${\phi_{k} = {\frac{{\overset{.}{N}}_{k\quad 2}}{{\overset{.}{N}}_{k\quad 1}} = \frac{\chi_{k} - \chi_{k - 1}}{1 - {2\quad\chi_{k - 1}}}}},$ k=1, 2 . . . , n and N_(ki) is a molar flow rate for combustor k for species i.

After the k-loop is performed, first with no regenerator and then with a regenerator, the cycle's performance, with and without regeneration, is evaluated by means of: $\begin{matrix} {{\overset{.}{m}}_{2} = {{\sum\limits_{k = 1}^{n}{\overset{.}{m}}_{k\quad 2}} = {W_{2}\chi_{n}}}} & (11) \\ {\left( \frac{{\overset{.}{m}}_{out}}{{\overset{.}{m}}_{i\quad n}} \right)_{1} = {1 - {2\quad\chi_{n}}}} & (12) \\ {{\overset{.}{Q}}_{i\quad n} = {\sum\limits_{k = 1}^{n}{\overset{.}{Q}}_{k}}} & (13) \\ {{\overset{.}{W}}_{net} = {{\sum\limits_{k = 1}^{n}{\overset{.}{W}}_{tk}} - {\overset{.}{W}}_{c}}} & (14) \\ {\eta_{cyc} = \frac{{\overset{.}{W}}_{net}}{{\overset{.}{Q}}_{i\quad n}}} & (15) \end{matrix}$ In the above, {dot over (m)}₂ is the total methane flow rate for 1 kmol/s of oxygen. The mass flow ratio given by Eq. (12) is for oxygen, i.e., it represents the fraction of initial oxygen that exits the last turbine. The other three parameters are self-evident.

When the BCP is a pump, set $\begin{matrix} {{{\overset{.}{W}}_{c} = {\sum\limits_{k = 1}^{n}{\overset{.}{W}}_{tk}}}{or}} & \left( {16a} \right) \\ {{\eta_{cyc} = 0}{and}{P_{t} = \left( {\frac{p_{102}}{p_{a}}P_{c}} \right)^{\frac{1}{n}}}} & \left( {16b} \right) \end{matrix}$ The efficiency condition is only approximately satisfied, i.e., 0≦η_(cyc)≦0.015   (17) On the other hand, when the BCP is an APU, set p₁₀₂=p_(a)   (18) and the turbine pressure ratio becomes P_(t)=P_(c) ^(1/n)   (19)

Except when noted, a number of model input parameters are held fixed, i.e., T₁₀₂=300 K, T_(m)=1500 K, η_(c)=0.85, η_(c)=0.85, η_(rg)=0.8 A given set of input parameters is used to compute both the non-regenerative and regenerative approaches for n=1, 2, and 3, for a total of six cases. While many hundreds of cases were computed, results are presented for only a select few. A major reason for the large number of cases is that condition (17) is not readily attained. In the pump mode, many cases had a negative cycle efficiency. Preference is given to n=1, or, if necessary, to n=2 cases. A low n value, of course, represents a relatively compact, low-weight BCP. Sea-Level Operation

Two nominal pump cases are selected; one without regeneration, the other with. At sea-level, the ambient pressure, p_(a), is nominally 10⁵ Pa. Aside from parameter values that have already been specified, the input for these nominal cases is given in Table 2. The corresponding performance is provided in Table 3. TABLE 2 Nominal Cases for a Sea-Level BCP Parameter no regeneration regeneration n 2 2 p102 (Pa) 2 × 10⁴ 2 × 10⁴ p102 (Torr) 150 150 Pc 17 18

TABLE 3 Output for Table 2 Nominal Cases Parameter no regeneration regeneration η_(cyc) 1.906 × 10⁻³ 1.268 × 10⁻² ${\overset{.}{m}}_{2}\quad\left( {{kg}\text{/}s} \right)$ 0.7575 0.3914 $\left( \frac{{\overset{.}{m}}_{out}}{{\overset{.}{m}}_{in}} \right)_{1}$ 0.9056 0.9512 T_(x) (K) — 1253 T_(y) (K) — 881.8 With p₁₀₂ and p_(a) equal to 2×10⁴ and 10⁵ Pa, respectively, and no regeneration, a value of n=2 and P_(c)=17 is required for a slightly positive η_(cyc). With regeneration, a slightly larger P_(c) value is required for a positive η_(cyc). The advantage of regeneration, however, becomes evident when the values for the methane flow rates are compared. (The value of regeneration is reconsidered shortly.) The regenerator case only requires 51.7% of the fuel required for the non-regenerator BCP. Note that the regenerator cycle efficiency, while still small, is larger than its non-regenerator counterpart. The main reason for this is the sharp reduction of {dot over (Q)}_(in) for the regenerator cycle. This is a general result that frequently occurs.

In both nominal cases, a reduction in either n or P_(c) results in a negative efficiency. For example, with n=1, none of the computed cycles, regardless of regeneration or the P_(c) value, has a positive cycle efficiency. In this circumstance, the required compressor power exceeds the available power from a single turbine unit. (This result, of course, depends on the value of the compressor and turbine efficiencies.)

The methane mass flow rate is quite small compared to the oxygen inlet flow rate. For example, it is only 2.4% of the oxygen mass flow rate when there is no regeneration. The small mass, or molar, methane flow rates are also evident by examining the oxygen ({dot over (m)}_(out)/{dot over (m)}_(in))₁ ratio. In the non-regenerator case, only 10% of the oxygen is burned, with half this value when a regenerator is used. These fractions are typical of many other cases. This is why the pumping or APU approaches, discussed here, works with a COIL that may buffer the singlet oxygen with a considerable amount of diluent.

Table 4 shows results for a p₁₀₂ scan in which first n, then P_(c), is minimized with the object of producing a slightly positive cycle efficiency. For the three cases shown, the efficiency first becomes positive for a cycle without regeneration. The 2×10⁴ case is the same as the no-regenerator case in Tables 1 and 2. Note the dramatic change in the BCP as p₁₀₂ increases. The p₁₀₂=1.5×10⁴ Pa case has a large compressor pressure ratio, which would require two centrifugal stages and intercooling. The table demonstrates the advantage of a COIL with a high SOG pressure, minimal stagnation pressure loss in the laser nozzle and optical cavity, and an efficient diffuser. TABLE 4 Inlet Pressure Scan for a Sea-Level BCP p102 (Pa) Parameter 1.5 × 10⁴ 2 × 10⁴ 2.5 × 10⁴ regenerator no no no n 3 2 1 P_(c) 50 17 11 η_(cyc) 4.512 × 10⁻³ 1.906 × 10⁻³ 1.024 × 10⁻³ m_(2 (kg/s)) 0.7468 0.7575 0.6757 There is little variation in the methane mass flow rate because of a trade-off in the amount of fuel required for the first combustor 54 versus the number of combustors. When P_(c) is large, the temperature difference, T_(m)-T₁₀₄, is relatively small, but now there are three combustors requiring fuel. On the other hand, when P_(c) is small, only one combustor is needed, but T_(m)-T₁₀₄ is large.

A sensitivity evaluation is performed based on the non-regenerative case of Tables 2 and 3. Results are shown in Table 5, where the input has nominal values, except for the parameter to be varied. The cycle efficiency and methane mass flow rate have their expected trends, although the magnitude of the change with T_(m) is large, as is the magnitude of the change in η_(cyc) when η_(c)=η_(t) is varied. TABLE 5 Sea-Level BCP Sensitivity Parameter η_(cyc) m_(2 (kg/s)) T₇ = 280 K   2.356 × 10⁻² 0.7893 = 320 K −2.154 × 10⁻² 0.7259 T_(m) = 1400 K −2.673 × 10⁻² 0.6597 = 1600 K   2.428 × 10⁻² 0.8584 η_(c) = η_(t) = 0.8 −4.199 × 10⁻² 0.7318 = 0.9   4.061 × 10⁻² 0.7813 150 Torr Operation

The ambient pressure is assumed to be 2×10⁴ Pa (150 Torr). A series of cases are shown in Table 6, where the BCP inlet pressure is either 10⁴ Pa (75 Torr) or 1.333×10⁴ Pa (100 Torr). The cases where η_(cyc) is small are pure pumping cases; the others are pumping plus APU cases. The regenerator cases all assume η_(rg)=0.8 and have the same p₁₀₂, p_(a), P_(c), and P_(t) values as their non-regenerator counterparts. Note the significant drop in the methane flow rate when a regenerator is used. The use of a regenerator substantially increases the cycle efficiency, but slightly decreases the net power output. As noted, the reason for this is that the heat input, {dot over (Q)}_(in), is substantially reduced. A net power of 7×10³ kW is quite large, but this is because the inlet oxygen flow rate was arbitrarily set at 1 kmol/s. Because p_(a)/p₁₀₂ is small, only cycles with a single turbine stage need be considered. From a COIL system viewpoint it is unlikely that a regenerator would be used. As just a pump, the BCP consists of a relatively low-pressure ratio compressor, a combustor, and a single-stage turbine whose pressure ratio is (p₁₀₂Pc)/p_(a). The resulting system should be quite compact and lightweight. TABLE 6 Performance when the Ambient Pressure is 150 Torr and n = 1 p₁₀₂ (Pa) P_(c) regenerator η_(cyc) {dot over (W)}_(net(kW)) {dot over (m)}_(2(kg/s)) 10⁴ 3 no 1.356 × 10⁻² 5.474 × 10² 0.8131 yes 3.514 × 10⁻² 3.934 × 10² 0.2399 10 no 0.1638 5.524 × 10³ 0.6875 yes 0.2860 5.204 × 10³ 0.3833 1.333 × 10⁴ 1.8 no 2.762 × 10⁻³ 1.177 × 10² 0.8551 yes 4.067 × 10⁻³ 4.033 × 10  0.2132 10 no 0.2276 7.675 × 10³ 0.6875 yes 0.3687 7.343 × 10³ 0.4179

Table 7 provides a P_(c) scan when p_(a)=150 Torr, p₁₀₂=75 Torr, and n=1. The cycle efficiency, with or without regeneration, increases with P_(c). The efficiency, however, has a maximum value for a larger P_(c) value than shown in the table. Again, the difference in the efficiency, between non-regenerator and regenerator cases, stems from the reduction in {dot over (Q)}_(in) when regeneration is used. Note that the difference in {dot over (m)}₂ values, regeneration versus non-regeneration, decreases with P_(c). As noted earlier, the effectiveness of regeneration decreases with P_(c). TABLE 7 Performance when the Ambient Pressure is 150 Torr, the Inlet Pressure is 75 Torr, and n = 1 P_(c) regenerator η_(cyc) W_(net, kW) m_(2, kg/s) 2.5 no −1.549 × 10⁻²   −6.383 × 10²   0.8967 yes −7.331 × 10⁻²   −7.292 × 10²   0.2138 3 no 1.356 × 10⁻² 5.474 × 10² 0.8131 yes 3.514 × 10⁻² 3.934 × 10² 0.2399 4 no 5.610 × 10⁻² 2.186 × 10³ 0.7867 yes 0.1494 1.952 × 10³ 0.2786 6 no 0.1091 4.015 × 10³ 0.7458 yes 0.2397 3.712 × 10³ 0.3284 8 no 0.1417 4.974 × 10³ 0.7139 yes 0.2727 4.652 × 10³ 0.3603 10 no 0.1638 5.524 × 10³ 0.6875 yes 0.2860 5.204 × 10³ 0.3833 Space Operation

For space operation, only the APU mode need be considered. This mode is useful only if the satellite has a substantial need for power during the short intervals that COIL is operational. The APU mode uses Eq. (18) and, in view of the importance of weight, only n=1 is considered.

For a given P_(c) value, the parameters of interest η_(cyc), {dot over (W)}_(net), {dot over (m)}₂

are independent of the p_(a) value, which can be taken as the inlet pressure, p₁₀₂. Table 8 shows a case with P_(c)=12. The only advantage for regeneration is the reduction in the methane flow rate. The efficiency increase is due, again, to a decrease in {dot over (Q)}_(in). For a large COIL device, with an oxygen flow rate of 0.1 kmol/s, a BCP has the potential for producing approximately 1 MW of power. TABLE 8 APU Performance for a BCP in Space with P_(c) = 12 and n = 1 regenerator η_(cyc) W_(net (kW)) m_(2 (kg/s)) no 0.3256 1.059 × 10⁴ 0.6647 yes 0.4492 1.029 × 10⁴ 0.4776

In any of the foregoing modes of operation (sea-level, 150 Torr, and space operation), a regenerator typically reduces the BCP fuel flow rate. In a COIL system, however, the fuel flow rate, with or without regeneration, is negligible compared to the SOG BHP flow rate (it is well below 1% of the BHP mass flow rate in the no-regenerator case). As a consequence, the hardware and benefits associated with regeneration are not warranted.

The use of a BCP according to the present invention makes possible, for the first time, to operate a high-power COIL at sea-level and lower altitudes for extended periods and significantly improves COIL operation at higher altitudes.

Having thus described the present invention by reference to certain of its preferred embodiments, it is noted that the embodiments disclosed are illustrative rather than limiting in nature and that a wide range of variations, modifications, changes, and substitutions are contemplated in the foregoing disclosure and, in some instances, some features of the present invention may be employed without a corresponding use of the other features. Many such variations and modifications may be considered obvious and desirable by those skilled in the art based upon a review of the foregoing description of preferred embodiments. Accordingly, it is appropriate that the appended claims be construed broadly and in a manner consistent with the scope of the invention. 

1. A gas laser comprising: a supply of fluid; a nozzle for accelerating supplied fluid to high velocity; a laser cavity coupled to the nozzle, wherein the accelerated fluid is employed as a laser gain medium; and a gas cycle outlet pump having an inlet coupled to the laser cavity, the gas cycle outlet pump employing the fluid from the laser cavity as a component of a process fluid in a gas cycle to raise the static pressure of the accelerated fluid.
 2. The laser according to claim 1, wherein the gas cycle outlet pump comprises a Brayton cycle outlet.
 3. The laser according to claim 1, wherein the gas cycle outlet pump comprises: a compressor having an inlet and an outlet, the inlet coupled to the laser cavity; a combustor having an inlet and an outlet, the combustor inlet coupled to the outlet of the compressor; and a turbine having an inlet and an outlet, the turbine inlet coupled to the outlet of the combustor, wherein the turbine powers the compressor.
 4. The laser according to claim 1, wherein the gas cycle outlet pump comprises multiple stages.
 5. The laser according to claim 1 further comprising a diffuser between the laser cavity and the gas cycle outlet pump.
 6. The laser according to claim 1, wherein the gas cycle outlet pump includes at least one reheat stage.
 7. The laser according to claim 3, wherein the compressor is a multi-stage compressor.
 8. The laser according to claim 3, wherein the turbine is a multi-stage turbine.
 9. The laser according to claim 1, wherein the gas cycle outlet pump includes a regeneration stage.
 10. The laser according to claim 1, wherein the gas cycle outlet pump includes an intercooling stage.
 11. The laser according to claim 3, wherein the turbine has a work output that exceeds the work required to operate the compressor, wherein there is net work output from the gas cycle pump.
 12. A gas laser comprising: a supply of fluid; a nozzle for accelerating supplied fluid to high velocity; a laser cavity coupled to the nozzle, wherein the accelerated fluid is employed as a laser gain medium; and a heat engine outlet pump having an inlet coupled to the laser cavity, the heat engine outlet pump employing the fluid from the laser cavity as a component of a process fluid in a heat engine to raise the static pressure of the accelerated fluid.
 13. The laser according to claim 12, wherein the heat engine outlet pump comprises a Brayton cycle outlet.
 14. The laser according to claim 12, wherein the heat engine outlet pump comprises: a compressor having an inlet and an outlet, the inlet coupled to the laser cavity; a combustor having an inlet and an outlet, the combustor inlet coupled to the outlet of the compressor; and a turbine having an inlet and an outlet, the turbine inlet coupled to the outlet of the combustor, wherein the turbine powers the compressor.
 15. The laser according to claim 12, wherein the heat engine outlet pump comprises multiple stages.
 16. The laser according to claim 12 further comprising a diffuser between the laser cavity and the heat engine outlet pump.
 17. The laser according to claim 12, wherein the heat engine outlet pump includes at least one reheat stage.
 18. The laser according to claim 14, wherein the compressor is a multi-stage compressor.
 19. The laser according to claim 14, wherein the turbine is a multi-stage turbine.
 20. The laser according to claim 12, wherein the heat engine outlet pump includes a regeneration stage.
 21. The laser according to claim 12, wherein the heat engine outlet pump includes an intercooling stage.
 22. The laser according to claim 14, wherein the turbine has a work output that exceeds the work required to operate the compressor, wherein there is net work output from the heat engine pump. 